JP2015152147A - Slide bearing and rotary machine equipped with same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a slide bearing capable of suppressing a trouble that a resin material of a surface layer is burned by frictional heat generated on a slide surface.SOLUTION: A slide bearing comprises: a rotor that includes a shaft 30a rotating about an axis; and a journal bearing member 11 supporting a load applied to the rotor by forming a lubricating oil film between the shaft 30a and the journal bearing member 11, the bearing member 11 including a lining layer 11a which is a slide surface contacting with an outer peripheral surface of the rotor and is formed with a resin material; and a back metal layer 11c supporting the lining layer 11a and formed out of a metallic material, the lining layer 11a in a rear edge 11e of the bearing member 11 being thinner than the lining layer 11a in a front edge 11d of the bearing member 11.

Description

  The present invention relates to a plain bearing and a rotary machine including the same.

  Journal bearings and thrust bearings are known as slide bearings used in rotating machines including a rotor that rotates around an axis. The journal bearing is a bearing that supports a load in a radial direction orthogonal to the axial direction of the rotor. The thrust bearing is a bearing that supports a load in the axial direction of the rotor.

These plain bearings generally use a bearing member provided with a lining layer (hereinafter referred to as a surface layer) that forms a sliding surface on a back metal (hereinafter referred to as a back layer) such as steel or chrome copper. is there. As a member for forming the surface layer, for example, white metal that is an alloy of lead and cast iron is used. In recent years, resin materials such as tetrafluoroethylene (PTFE) and polyetherketone (PEEK) having a lower friction coefficient and higher wear resistance than white metal are sometimes used as members for forming the surface layer. is there.
Patent Document 1 discloses a plain bearing in which a surface layer formed of white metal or synthetic resin is detachably attached to a back surface layer.

JP 2005-1114019 A

  In the plain bearing in which the surface layer is formed of a resin material, the heat conductivity of the resin material is 1/10 or less of that of white metal, so that the frictional heat generated on the sliding surface is not easily transmitted to the back layer. Therefore, there is a possibility that the resin material forming the surface layer of the slide bearing is burned out by frictional heat generated on the sliding surface. If the surface layer of the sliding bearing is damaged by burning, the sliding bearing cannot support the rotor, which may cause damage to the rotor or stop operation of the rotary machine including the rotor.

  The present invention has been made in view of such circumstances, and suppresses a problem that the resin material is burned out by frictional heat generated on the sliding surface while the surface layer of the slide bearing is formed of the resin material. An object of the present invention is to provide a plain bearing and a rotating machine including the same.

In order to achieve the above object, the present invention employs the following means.
A plain bearing according to the present invention supports a load applied to the rotor by forming a lubricating fluid film between the rotor having a rotating part that rotates about an axis and a fixed member and the rotating part. A sliding bearing comprising a bearing member, the bearing member being a sliding surface in contact with the outer peripheral surface of the rotor and a surface layer formed of a resin material, and supporting the surface layer and formed of a metal material And the thickness of the surface layer at the rear edge of the bearing member is smaller than the thickness of the surface layer at the front edge of the bearing member.

  According to the slide bearing according to the present invention, the surface layer of the bearing member formed of the resin material becomes a sliding surface in contact with the outer peripheral surface of the rotor. The bearing member supports a load applied to the rotor by forming a film of lubricating fluid between the rotor and the rotating portion of the rotor. The pressure generated by the lubricating fluid to support the load applied to the rotor is higher at the rear edge of the bearing member than at the front edge of the bearing member, and accordingly the temperature at the front edge of the sliding surface. The temperature at the trailing edge of the sliding surface is higher.

According to the slide bearing according to the present invention, the thickness of the surface layer at the rear edge of the bearing member is thinner than the thickness of the surface layer at the front edge of the bearing member. Heat of the surface layer is easily transferred to the back layer formed of a metal material. Therefore, the temperature of the surface layer at the rear edge portion of the bearing member that is easily affected by frictional heat can be reduced.
By doing in this way, the slide bearing which suppressed the malfunction which the resin material burns out by the frictional heat which generate | occur | produced on the sliding surface can be provided, forming the surface layer of a slide bearing with a resin material.

In the plain bearing according to the first aspect of the present invention, the bearing member includes an intermediate layer formed of a metal material between the surface layer and the back layer, and the hardness of the metal material forming the intermediate layer is: It is characterized by being lower than the hardness of the metal material forming the back layer.
By doing in this way, when the surface layer formed of the resin material disappears due to wear or peeling, the outer peripheral surface of the rotor does not contact the metal material of the back layer, and the hardness is lower than that of the back layer. The metal material of the intermediate layer is in contact with the outer peripheral surface of the rotor.
Therefore, the frictional heat generated on the sliding surface is transmitted to the intermediate layer formed of the metal material, and the outer peripheral surface of the rotor is prevented from being in contact with the high-hardness metal material of the back surface layer. Can do.

The sliding bearing according to the second aspect of the present invention is characterized in that the thickness of the surface layer gradually decreases from the front edge portion toward the rear edge portion.
By doing so, the frictional heat transfer efficiency from the front surface layer to the back surface layer gradually increases from the front edge portion of the bearing member toward the rear edge portion of the bearing member, and the temperature at the rear edge portion of the bearing member decreases. Can be made.

In the slide bearing according to the third aspect of the present invention, a plurality of the bearing members are arranged around the axis along the outer peripheral surface of the rotor, and the outer peripheral surface of the rotor is supported by the plurality of bearing members. It is characterized by.
In this way, in the journal bearing that supports the outer peripheral surface of the rotor with a plurality of bearing members arranged at intervals around the axis of the rotor, the surface layer is formed of a resin material and is generated on the sliding surface. It is possible to suppress a problem that the resin material is burned out by the frictional heat.

In the plain bearing of the above aspect, the thickness of the surface layer at the central portion in the axial direction of the rear edge portion may be thinner than the thickness of the surface layer at the front edge portion.
By doing in this way, the frictional heat which is easy to accumulate | store in the axial center part of the rear edge part of a sliding surface can be made easy to be transmitted from a surface layer to a back layer.

A plain bearing according to a fourth aspect of the present invention includes a thrust collar for the rotor to transmit a load acting in the axial direction to the bearing member, and the axial line along an end surface of the thrust collar in the axial direction. A plurality of the bearing members are arranged around the periphery, and the axial end surfaces of the thrust collar are supported by the plurality of bearing members.
In this way, in the thrust bearing that supports the axial end surface of the thrust collar provided in the rotor with a plurality of bearing members arranged at intervals around the axis of the rotor, the surface layer is formed of a resin material. The problem that the resin material is burned out by frictional heat generated on the sliding surface can be suppressed.

  In the sliding bearing of the above aspect, the thickness of the surface layer on the inner peripheral side of the rear edge is thinner than the thickness of the surface layer on the inner peripheral side of the front edge, and the outer peripheral side of the front edge The thickness of the surface layer and the thickness of the surface layer on the outer peripheral side of the rear edge portion may be thinner than the thickness of the surface layer on the inner peripheral side of the front edge portion, respectively.

In the thrust bearing, the moving speed in the circumferential direction is faster on the outer peripheral side than the inner peripheral side of the sliding surface, and more frictional heat is generated on the outer peripheral side than on the inner peripheral side of the sliding surface.
Therefore, with the above-described configuration, on the inner peripheral side of the sliding surface, the thickness of the surface layer at the rear edge is made thinner than the thickness of the surface layer at the front edge, and is affected by frictional heat. The temperature of the surface layer at the rear edge of the sliding surface that is easy to slide can be lowered. In addition, the thickness of the surface layer on the outer peripheral side of the sliding surface is made thinner than the thickness of the surface layer on the inner peripheral side of the front edge of the bearing member, and frictional heat generated on the outer peripheral side of the sliding surface is It can be easily transmitted from the layer to the back layer.

A rotating machine according to the present invention includes any of the slide bearings described above.
According to the rotating machine according to the present invention, it is possible to suppress the problem that the resin material is burned out by the frictional heat generated on the sliding surface while the surface layer of the slide bearing is formed of the resin material.

  ADVANTAGE OF THE INVENTION According to this invention, while forming the surface layer of a sliding bearing with a resin material, the sliding bearing which suppressed the malfunction which a resin material burns out by the frictional heat which generate | occur | produced on the sliding surface, and a rotary machine provided with the same are provided. can do.

It is a perspective view which shows the slide bearing of 1st Embodiment. It is sectional drawing of the journal bearing shown in FIG. 1, Comprising: It is sectional drawing in the plane orthogonal to the axis line of a rotor. It is the elements on larger scale of the journal bearing member shown in FIG. FIG. 4 is a perspective view of a journal bearing member shown in FIG. 3. It is the figure which looked at the thrust bearing shown in FIG. 1 from the end surface side of the thrust collar along the axis. FIG. 6 is a cross-sectional view of the bearing member shown in FIG. It is a perspective view of the thrust bearing member shown in FIG. It is a graph which shows the relationship between the pressure of an oil film with respect to the distance from the entrance part of the sliding surface of a bearing member, and the surface temperature of a sliding surface. It is sectional drawing which shows the journal bearing of 2nd Embodiment, Comprising: It is sectional drawing in the plane orthogonal to the axis line of a rotor. It is sectional drawing which shows a part of thrust bearing of 2nd Embodiment. It is a perspective view which shows the journal bearing of 3rd Embodiment. It is a perspective view which shows the thrust bearing of 3rd Embodiment.

[First Embodiment]
Hereinafter, a plain bearing according to a first embodiment of the present invention and a rotary machine including the same will be described with reference to the drawings.
As shown in FIG. 1, the plain bearing of the present embodiment is a bearing member that supports a load applied to the rotor 30, and includes a journal bearing 10 and a thrust bearing 20. The rotating machine of the present embodiment includes the above-described slide bearing, and is a device such as a steam turbine or a gas turbine. The rotary machine of this embodiment is connected to a rotor 30 whose load is supported by a slide bearing.

  The rotor 30 includes a shaft portion 30a (rotating portion) and a thrust collar 30b (rotating portion), each of which rotates about the axis A. The thrust collar 30b is a substantially disk-shaped member having an outer diameter larger than that of the shaft portion 30a. The thrust collar 30b is arranged so that a plurality of bearing members constituting the thrust bearing 20 are opposed to both end surfaces in the axis A direction. The

  In FIG. 1, illustration of a support ring 40 (fixed member) to which the journal bearing 10 is fixed and a support member 50 (fixed member) to which the thrust bearing 20 is fixed is omitted. As shown in FIG. 2, the journal bearing 10 is fixed to the support ring 40, and slides with the outer peripheral surface of the rotor 30 in contact with the sliding surface of the journal bearing 10. Further, as shown in FIGS. 5 and 6, the thrust bearing 20 is fixed to the support member 50, and slides with the outer peripheral surface of the rotor 30 in contact with the sliding surface of the thrust bearing 20. Yes.

Here, the journal bearing 10 of this embodiment which is a slide bearing will be described.
As shown in FIGS. 1 and 2, the journal bearing 10 includes a plurality of journal bearing members 11, 12, 13, and 14 that are arranged around the axis A along the outer peripheral surface of the shaft portion 30 a of the rotor 30. (Bearing member). The outer peripheral surface of the shaft portion 30 a of the rotor 30 is supported by a plurality of journal bearing members 11, 12, 13, and 14.
As shown in FIG. 2, the plurality of journal bearing members 11, 12, 13, and 14 are supported by a support ring 40 (fixed member) fixed to an installation surface (not shown).

  Among the plurality of journal bearing members 11, 12, 13, and 14, the journal bearing member 11 and the journal bearing member 12 are installed vertically downward, and the journal bearing member 13 and the journal bearing member 14 are installed vertically upward. ing. The load directed downward in the vertical direction applied by the weight of the rotor 30 is supported by the journal bearing member 11 and the journal bearing member 12.

  Each of the journal bearing members 11, 12, 13, and 14 is supplied with lubricating oil (lubricating fluid) by a lubricating oil supply mechanism (not shown), and the lubricating oil is fed to each journal bearing member 11, 12, 13, and 14 and the rotor. 30 is supplied to the gap between the outer peripheral surface of the shaft portion 30a. A lubricating oil film is formed between the journal bearing members 11, 12, 13, and 14 and the shaft portion 30 a of the rotor 30 by the lubricating oil supplied to the gap. The lubricating oil film generates a pressure that presses the outer peripheral surface of the shaft portion 30 a toward the axis A of the rotor 30. The journal bearing members 11, 12, 13, and 14 support the load applied to the shaft portion 30a using the pressure generated by the lubricating oil.

  FIG. 3 is a partially enlarged view of the journal bearing member 11 shown in FIG. Although the journal bearing member 11 is illustrated in FIG. 3, the journal bearing members 12, 13, and 14 are assumed to have the same configuration as the journal bearing member 11. In FIG. 3, the arrow written on the shaft portion 30 a of the rotor 30 indicates the rotation direction around the axis A of the rotor 30. The outer peripheral surface of the shaft portion 30a moves from the front edge portion 11d of the sliding surface shown in FIG. 3 toward the rear edge portion 11e as the rotor 30 rotates around the axis A. Thus, the front edge portion 11 d is located on the upstream side in the rotational direction around the axis A of the rotor 30, and the rear edge portion 11 e is located on the downstream side in the rotational direction around the axis A of the rotor 30.

  As shown in FIG. 3, the journal bearing member 11 has a lining layer 11a (surface layer), an intermediate layer 11b, and a back metal layer 11c (back layer) from the side close to the outer peripheral surface of the shaft portion 30a of the rotor 30. It has a laminated three-layer structure. The lining layer 11a is a layer that becomes a sliding surface in contact with the outer peripheral surface of the shaft portion 30a, and is formed of a resin material. As the resin material, for example, tetrafluoroethylene (PTFE), polyetherketone (PEEK), or the like can be used.

The back metal layer 11c is a layer that supports the lining layer 11a and the intermediate layer 11b, and is formed of a metal material. As the metal material, an iron-based metal material, a copper-based metal material, or the like can be used.
The intermediate layer 11b is a layer formed between the lining layer 11a and the back metal layer 11c, and is formed of a metal material. A copper-based metal material or the like can be used as the metal material. The hardness of the metal material used for the intermediate layer 11b is lower than the hardness of the metal material used for the back metal layer 11c. The reason why the hardness of the metal material used for the intermediate layer 11b is lowered is that the shaft portion 30a is prevented from being damaged when the lining layer 11a disappears due to wear or peeling and the shaft portion 30a contacts the intermediate layer 11b. It is to do.

  As shown in FIG. 3, in the journal bearing member 11 of the present embodiment, the thickness h2 of the lining layer 11a at the rear edge portion 11e of the sliding surface formed by the lining layer 11a is such that the leading edge portion 11d of the sliding surface. Is thinner than the thickness h1 of the lining layer 11a.

Although various thicknesses can be adopted as the thickness h1 of the lining layer 11a, for example, a thickness of several mm is desirable. Further, various thicknesses can be adopted as the thickness of the intermediate layer 11b in the thickness h1 portion of the lining layer 11a. For example, the same thickness as the thickness h1 is desirable.
Further, as shown in FIG. 3, the total thickness of the lining layer 11 a and the intermediate layer 11 b is desirably constant on the sliding surface along the circumferential direction of the rotor 30.

  When the length of the sliding surface along the circumferential direction of the rotor 30 is L, the thickness of the lining layer 11a from the front edge portion 11d to the position where the distance from the front edge portion 11d is L / 2 is h1. It is constant at. Similarly, the thickness of the lining layer 11a up to a position where the distance from the rear edge portion 11e is L / 2 is constant at h2. Various values can be used as the value of h1 and the value of h2, but h2 is approximately half the thickness of h1.

  As shown in FIG. 3, the thickness h2 of the lining layer 11a at the trailing edge portion 11e of the sliding surface is made thinner than the thickness h1 of the lining layer 11a at the leading edge portion 11d of the sliding surface. This is because the heat of the lining layer 11a, which becomes high on the trailing edge 11e side, is easily transferred to the intermediate layer 11b and the back metal layer 11c.

  A region where the thickness of the lining layer 11a is h2 is a region indicated by oblique lines in the perspective view of FIG. The arrows shown in FIG. 4 indicate the rotation direction of the shaft portion 30 a of the rotor 30. As shown in FIG. 4, the hatched region where the thickness of the lining layer 11 a is h <b> 2 extends in the direction of the axis A perpendicular to the rotation direction of the shaft portion 30 a of the rotor 30.

  As shown in an example in FIG. 8, the oil film of the lubricating oil formed on the sliding surface is closer to the rear edge portion 11e (distance L) of the sliding surface of the journal bearing member 11 from the front edge portion 11d. The pressure increases. In FIG. 8, the position where the pressure Pmax is the position where the oil film pressure is highest. Further, as the pressure of the lubricating oil film increases, the distance from the front edge portion 11d of the sliding surface of the journal bearing member 11 is closer to the rear edge portion 11e (distance L). The surface temperature increases. In FIG. 8, the position where the temperature becomes Tmax is the position where the surface temperature of the sliding surface becomes the highest.

  In the example shown in FIG. 3, the thickness of the lining layer 11 a is switched at a position where the distance from the front edge portion 11 d is half of the total length L of the sliding surface, but other modes may be used. For example, the thickness of the lining layer 11a may be switched at a position closer to the rear edge portion 11e.

Next, the thrust bearing 20 of this embodiment which is a slide bearing will be described.
As shown in FIGS. 1 and 5, the thrust bearing 20 includes a plurality of thrust bearing members 21, 22 arranged at intervals around the axis A along the end surface in the direction of the axis A of the thrust collar 30 b of the rotor 30. 23, 24 (bearing member). The end surface of the thrust collar 30b shown in FIG. 1 on the thrust bearing 20 side is supported by a plurality of thrust bearing members 21, 22, 23, and 24.

FIG. 5 shows an example in which the four thrust bearing members 21, 22, 23, 24 are arranged around the axis A at intervals, but the number of thrust bearing members having a short circumferential length is four or more. It may be arranged.
The plurality of thrust bearing members 21, 22, 23, and 24 are fixed to an annular support member 50 (fixing member) disposed to face the thrust collar 30 b.

  Lubricating oil (lubricating fluid) is supplied to each of the thrust bearing members 21, 22, 23, 24 by a lubricating oil supply mechanism (not shown), and the lubricating oil is supplied to each thrust bearing member 21, 22, 23, 24 and the rotor. 30 is supplied to the gap between the end surfaces of the 30 thrust collars 30b. A lubricating oil film is formed between the thrust bearing members 21, 22, 23, and 24 and the thrust collar 30 b of the rotor 30 by the lubricating oil supplied to the gap. The film of lubricating oil generates pressure that presses the end face of the thrust collar 30 b along the axis A of the rotor 30. The thrust bearing members 21, 22, 23, and 24 support the load applied to the thrust collar 30b by using the pressure generated by the lubricating oil.

  6 is a cross-sectional view of the thrust bearing member 21 shown in FIG. Although the thrust bearing member 21 is illustrated in FIG. 6, the thrust bearing members 22, 23, and 24 are assumed to have the same configuration as the thrust bearing member 21. In FIG. 6, the arrow described in the thrust collar 30b of the rotor 30 indicates the rotation direction around the axis A of the thrust collar 30b. The end surface of the thrust collar 30b moves from the front edge portion 21d of the sliding surface shown in FIG. 6 toward the rear edge portion 21e as the rotor 30 rotates about the axis A. Thus, the front edge portion 21d is located upstream in the rotational direction around the axis A of the thrust collar 30b, and the rear edge portion 21e is located downstream in the rotational direction around the axis A of the thrust collar 30b.

  A pivot 21 f is provided on the rear edge 21 e side of the back surface of the thrust bearing member 21. The thrust bearing member 21 is fixed to the support member 50 via a pivot 21f. The pivot 21f is a member for inclining the rear end 21e side of the thrust bearing member 21 so as to be close to the thrust collar 30b.

  As shown in FIG. 6, the thrust bearing member 21 includes a lining layer 21a (surface layer), an intermediate layer 21b, and a back metal layer 21c (back surface layer) laminated from the side close to the end face of the thrust collar 30b of the rotor 30. It has a three-layer structure. The lining layer 21a is a layer that becomes a sliding surface in contact with the end surface of the thrust collar 30b, and is formed of a resin material. As the resin material, for example, tetrafluoroethylene (PTFE), polyetherketone (PEEK), or the like can be used.

The back metal layer 21c is a layer that supports the lining layer 21a and the intermediate layer 21b, and is formed of a metal material. As the metal material, an iron-based metal material, a copper-based metal material, or the like can be used.
The intermediate layer 21b is a layer formed between the lining layer 21a and the back metal layer 21c, and is formed of a metal material. A copper-based metal material or the like can be used as the metal material. The hardness of the metal material used for the intermediate layer 21b is lower than the hardness of the metal material used for the back metal layer 21c. The reason why the hardness of the metal material used for the intermediate layer 21b is reduced is that the thrust collar 30b is prevented from being damaged when the lining layer 21a disappears due to wear or peeling and the thrust collar 30b contacts the intermediate layer 21b. It is to do.

  As shown in FIG. 6, in the thrust bearing member 21 of the present embodiment, the thickness h4 of the lining layer 21a at the rear edge portion 21e of the sliding surface formed by the lining layer 21a is such that the leading edge portion 21d of the sliding surface. Is thinner than the thickness h3 of the lining layer 21a.

Although various thicknesses can be adopted as the thickness h3 of the lining layer 21a, for example, a thickness of several mm is desirable. Various thicknesses can be adopted as the thickness of the intermediate layer 21b in the thickness h3 portion of the lining layer 21a. For example, the thickness is preferably the same as the thickness h3.
Further, as shown in FIG. 6, the total thickness of the lining layer 21 a and the intermediate layer 21 b is desirably constant on the sliding surface along the circumferential direction of the rotor 30.

  When the length of the sliding surface along the circumferential direction of the rotor 30 is L, the thickness of the lining layer 21a from the front edge 21d to the position where the distance from the front edge 21d is L / 2 is h3. It is constant at. Similarly, the thickness of the lining layer 21a up to a position where the distance from the rear edge portion 21e is L / 2 is constant at h4. Various values can be used as the value of h3 and the value of h4, but h4 is approximately half the thickness of h3.

  As shown in FIG. 6, the thickness h4 of the lining layer 21a at the trailing edge 2e of the sliding surface is made thinner than the thickness h3 of the lining layer 21a at the leading edge 21d of the sliding surface. This is because the heat of the lining layer 21a, which becomes high on the rear edge 21e side, is easily transferred to the intermediate layer 21b and the back metal layer 21c.

  A region where the thickness of the lining layer 21a is h4 is a region indicated by oblique lines in the perspective view of FIG. The arrows shown in FIG. 7 indicate the direction of rotation of the thrust collar 30 b of the rotor 30. As shown in FIG. 7, the hatched region where the thickness of the lining layer 21 a is h <b> 2 extends in the radial direction of the rotor 30 perpendicular to the rotational direction of the thrust collar 30 b of the rotor 30.

As described above, the example shown in FIG. 8 relates to the journal bearing member 11, but the thrust bearing member 21 is also an example as shown in FIG.
As shown in FIG. 8, when the distance from the front edge 21d of the sliding surface of the thrust bearing member 21 is closer to the rear edge 21e (distance L), the pressure of the oil film of the lubricating oil formed on the sliding surface Becomes higher. In FIG. 8, the position where the pressure Pmax is the position where the oil film pressure is highest. As the oil film pressure of the lubricating oil increases, the distance from the front edge portion 21d of the sliding surface of the thrust bearing member 21 is closer to the rear edge portion 21e (distance L). The surface temperature increases. In FIG. 8, the position where the temperature becomes Tmax is the position where the surface temperature of the sliding surface becomes the highest.

  In the example illustrated in FIG. 6, the thickness of the lining layer 21 a is switched at a position where the distance from the front edge portion 21 d is half the total length L of the sliding surface, but other modes may be used. For example, the thickness of the lining layer 21a may be switched at a position closer to the rear edge portion 21e.

The operation and effect of the plain bearing of the present embodiment described above will be described.
According to the slide bearing (journal bearing 10 and thrust bearing 20) according to the present embodiment, the lining layer (surface layer) of the bearing member formed of a resin material becomes a sliding surface in contact with the outer peripheral surface of the rotor. The bearing member supports a load applied to the rotor 30 by forming a film of lubricating oil (lubricating fluid) between the rotating portion (the bearing portion 30a and the thrust collar 30b) of the rotor 30. The pressure generated by the lubricating oil to support the load applied to the rotor 30 is higher than the front edge (front edge 11d, front edge 21d) of the sliding surface than the rear edge (rear edge 11e) of the sliding surface. , The rear edge 21e) is higher, and accordingly, the temperature at the rear edge of the sliding surface is higher than the temperature at the front edge of the sliding surface.

According to the slide bearing (journal bearing 10, thrust bearing 20) according to the present embodiment, the thickness of the lining layer at the trailing edge of the sliding surface is thinner than the thickness of the lining layer at the leading edge of the sliding surface. Therefore, the heat at the rear edge of the sliding surface is easily transferred to the back metal layer (back surface layer) formed of the metal material. Therefore, the temperature at the trailing edge of the sliding surface that is easily affected by frictional heat can be reduced.
By doing in this way, the sliding bearing which suppressed the malfunction which the resin material burns out by the frictional heat which generate | occur | produced on the sliding surface can be provided, forming the linear layer of a sliding bearing with a resin material.

In the slide bearing of this embodiment, the bearing member includes an intermediate layer formed of a metal material between the lining layer and the back metal layer, and the hardness of the metal material forming the intermediate layer is a metal material that forms the back metal layer. Is lower than the hardness.
By doing in this way, when the lining layer formed of the resin material has disappeared due to wear or peeling, the hardness of the backing metal layer is not in contact with the metal material of the backing metal layer on the outer peripheral surface of the rotor 30. The low intermediate layer metal material comes into contact with the outer peripheral surface of the rotor 30.
Accordingly, the frictional heat generated on the sliding surface is transmitted to the intermediate layer formed of the metal material, and the trouble that the outer peripheral surface of the rotor 30 contacts and wears the metal material having a high hardness of the back metal layer is prevented. be able to.

In the journal bearing 10 of the present embodiment, a plurality of bearing members 11, 12, 13, and 14 are arranged around the axis A along the outer peripheral surface of the shaft portion 30a of the rotor 30, and the plurality of bearing members 11, 12, 13 and 14 support the outer peripheral surface of the shaft portion 30a of the rotor 30.
In this way, in the journal bearing 10 that supports the outer peripheral surface of the shaft portion 30a of the rotor 30 by the plurality of bearing members 11, 12, 13, and 14 arranged at intervals around the axis A of the rotor 30, While the lining layer 11a is formed of a resin material, it is possible to suppress a problem that the resin material is burned out by frictional heat generated on the sliding surface.

The thrust bearing 20 of the present embodiment includes a thrust collar 30b for the rotor 30 to transmit a load acting in the direction of the axis A to the bearing members 21, 22, 23, and 24, and an end surface of the thrust collar 30b in the direction of the axis A A plurality of bearing members 21, 22, 23, 24 are arranged around the axis A along the axis A, and the end surfaces of the thrust collar 30 b in the direction of the axis A are supported by the plurality of bearing members 21, 22, 23, 24. ing.
By doing in this way, the thrust surface which the end surface of the axial line A direction of the thrust collar 20b with which the rotor 30 is equipped is supported by the several bearing members 21, 22, 23, 24 arrange | positioned at intervals around the axial line A of the rotor 30 is supported. In the bearing 20, while the lining layer 21a is formed of a resin material, it is possible to suppress a problem that the resin material is burned out by frictional heat generated on the sliding surface.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to the drawings.
The second embodiment is a modification of the above-described first embodiment, and is the same as the first embodiment except for a part that will be specifically described below.
In the first embodiment, the thickness of the lining layer is switched in two steps between the front edge portion and the rear edge portion of the sliding surface of the bearing member. On the other hand, in the second embodiment, the thickness of the lining layer is gradually reduced from the front edge portion to the rear edge portion of the sliding surface of the bearing member.

The cross-sectional view of the journal bearing member 11 ′ shown in FIG. 9 corresponds to the cross-sectional view of the journal bearing member 11 shown in FIG. 3 of the first embodiment. In FIG. 3 of the first embodiment, the thickness of the lining layer 11a at the front edge portion 11d of the sliding surface of the lining layer 11a of the journal bearing member 11 is constant at h1, and the lining at the rear edge portion 11e of the sliding surface. The thickness of the layer 11a was constant at h2.
On the other hand, in FIG. 9 of the present embodiment, the thickness of the lining layer 11′a of the journal bearing member 11 ′ increases from the thickness h1 toward the rear edge portion 11e from the front edge portion 11d of the sliding surface. The thickness is gradually reduced to h2. Further, the thickness of the intermediate layer 11′b is changed from the front edge portion 11d of the sliding surface to the rear edge portion 11e so that the total thickness of the lining layer 11′a and the intermediate layer 11′b is constant. It gradually becomes thicker.

Further, the sectional view of the thrust bearing member 21 ′ shown in FIG. 10 corresponds to the sectional view of the thrust bearing member 21 shown in FIG. 6 of the first embodiment. In FIG. 6 of the first embodiment, the thickness of the lining layer 21a at the front edge portion 21d of the sliding surface of the lining layer 21a of the thrust bearing member 21 is constant at h2, and the lining at the rear edge portion 21e of the sliding surface. The thickness of the layer 21a was constant at h4.
On the other hand, in FIG. 10 of the present embodiment, the thickness of the lining layer 21′a of the thrust bearing member 21 ′ increases from the thickness h3 toward the rear edge portion 21e from the front edge portion 21d of the sliding surface. The thickness is gradually reduced to h4. Further, the thickness of the intermediate layer 21′b is changed from the front edge portion 21d of the sliding surface to the rear edge portion 21e so that the total thickness of the lining layer 21′a and the intermediate layer 21′b is constant. It gradually becomes thicker.

As described above, in the slide bearing (journal bearing, thrust bearing) of the present embodiment, the thickness of the lining layer (surface layer) is such that the front edge portion of the sliding surface (front edge portion 11d, front edge portion 21d). From the sliding surface toward the rear edge (rear edge 11e, rear edge 21e).
Thus, the frictional heat transfer efficiency from the lining layer to the back metal layer (back layer) is gradually increased from the front edge portion of the sliding surface to the rear edge portion of the sliding surface. The temperature of the surface layer at the trailing edge can be lowered.

[Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to the drawings.
The third embodiment is a modification of the above-described first embodiment, and is the same as the first embodiment, except for the portions specifically described below.

  In the journal bearing member 11 of the first embodiment, as shown in FIG. 4, the hatched region where the thickness of the lining layer 11a is h2 is in the direction of the axis A perpendicular to the rotation direction of the shaft portion 30a of the rotor 30. It was an extension. On the other hand, in the journal bearing member 11 ″ of the third embodiment, as shown in FIG. 11, the region indicated by the oblique line in which the thickness of the lining layer 11 ″ a is h2 is the journal bearing member in the direction of the axis A. 11 ″ is the central region.

  Accordingly, the thickness of the lining layer 11''a at the center in the axis A direction of the trailing edge 11e of the sliding surface of the lining layer 11''a is the end of the leading edge 11d of the sliding surface in the axis A direction. This is thinner than the thickness of the lining layer 11 ″ a in the portion. Further, the thickness of the intermediate layer 11 "b is adjusted so that the total thickness with the lining layer 11" a is constant.

  Further, in the thrust bearing member 21 of the first embodiment, as shown in FIG. 7, the hatched region where the thickness of the lining layer 21a is h4 is perpendicular to the rotational direction of the thrust collar 30b of the rotor 30. It extended in the radial direction. On the other hand, in the thrust bearing member 21 '' of the third embodiment, as shown in FIG. 12, the hatched region where the thickness of the lining layer 21''a is h4 is the lining layer 21''a. It is the area | region of the rear edge part 21e side and outer peripheral side of a sliding surface.

Therefore, the thickness of the lining layer 21''a on the inner peripheral side of the rear edge portion 21e of the sliding surface of the lining layer 21''a is equal to the lining layer 21 ′ on the inner peripheral side of the front edge portion 21d of the sliding surface. It is thinner than 'a'.
Further, the thickness of the lining layer 21 ″ a on the outer peripheral side of the front edge portion 21d of the sliding surface of the lining layer 21a, and the thickness of the lining layer 21 ″ a on the outer peripheral side of the rear edge portion 21e of the sliding surface. However, it is thinner than the thickness of the lining layer 21 ″ a on the inner peripheral side of the front edge portion 21d of the sliding surface.

As described above, in the journal bearing member 11 ″ of the present embodiment, the thickness of the lining layer 11 ″ a at the center portion in the axis A direction of the rear edge portion 11e of the sliding surface is the front of the sliding surface. It is thinner than the thickness of the lining layer 11 ″ a at the edge 11d.
By doing in this way, the frictional heat which is easy to accumulate | store in the center part of the axis line A direction of the trailing edge part 11e of a sliding surface can be made easy to be transmitted to a back surface layer. Further, there is a problem in that the lining layer 11''a disappears due to friction or peeling while ensuring the thickness of the lining layer 11''a at both ends in the axis A direction of the rear edge portion 11e of the sliding surface. Can be suppressed.

  Further, the thrust bearing member 21 '' of the present embodiment has a faster movement speed in the circumferential direction on the outer circumferential side than the inner circumferential side of the sliding surface, and more on the outer circumferential side than the inner circumferential side of the sliding surface. A lot of frictional heat is generated. Therefore, with the above-described configuration, the thickness of the lining layer 21 ″ a at the rear edge portion 21e is made larger than the thickness of the lining layer 21 ″ a at the front edge portion 21d on the inner peripheral side of the sliding surface. The temperature at the trailing edge 21e of the sliding surface that is easily affected by frictional heat can be lowered by reducing the thickness. Further, the thickness of the lining layer 21 ″ a on the outer peripheral side of the sliding surface is made thinner than the thickness of the lining layer 21 ″ a on the inner peripheral side of the front edge portion 21d of the sliding surface, so that the sliding surface It is possible to make it easier for the frictional heat generated on the outer peripheral side of the metal to be transferred to the back metal layer 21c.

[Other Embodiments]
In the journal bearing member 11 of the first embodiment, the area of the sliding surface of the lining layer 11a indicated by the oblique lines in FIG. 4 is set to a uniform thickness h2, but other modes may be used. For example, the thickness of the lining layer 11a at the edge in the area indicated by hatching (the part serving as the boundary with the space in which the journal bearing member 11 is disposed) is the same as that of other areas not indicated by hatching in FIG. It may be h1.
By doing in this way, the thickness of the lining layer 11a in the edge part of the journal bearing member 11 is ensured, and the malfunction that the edge lining layer 11a lose | disappears by friction and peeling can be suppressed.

In the thrust bearing member 21 of the first embodiment, the region of the sliding surface of the lining layer 21a indicated by hatching in FIG. 7 has a uniform thickness h4. Good. For example, the thickness of the lining layer 21a at the edge in the hatched region (the portion serving as the boundary with the space in which the thrust bearing member 21 is disposed) is the same as that of other regions not shown in hatched in FIG. It may be h3.
By doing in this way, the thickness of the lining layer 21a in the edge part of the thrust bearing member 21 is ensured, and the malfunction that the lining layer 21a of an edge part lose | disappears by friction and peeling can be suppressed.

Further, in the journal bearing member 11 '' of the third embodiment, the area of the sliding surface of the lining layer 11''a shown by hatching in FIG. 11 has a uniform thickness h2. An aspect may be sufficient. For example, the thickness of the lining layer 11 ″ a at the edge in the region indicated by the oblique lines (the portion that becomes the boundary with the space in which the journal bearing member 11 is disposed) is the same as in other regions not indicated by the oblique lines in FIG. It is good also as thickness h1.
By doing in this way, the thickness of the lining layer 11''a at the edge of the journal bearing member 11 '' is secured, and the lining layer 11''a at the edge disappears due to friction or peeling. Can be suppressed.

Further, in the thrust bearing member 21 '' of the third embodiment, the region of the sliding surface of the lining layer 21''a indicated by the oblique line in FIG. 12 has a uniform thickness h4. An aspect may be sufficient. For example, the thickness of the lining layer 21 ″ a at the edge in the region indicated by hatching (the portion serving as the boundary with the space where the thrust bearing member 21 ″ is disposed) is the other region not indicated by hatching in FIG. It is good also as thickness h3 similar to.
By doing in this way, the thickness of the lining layer 21''a at the edge of the thrust bearing member 21 '' is secured, and the problem that the lining layer 21''a at the edge disappears due to friction and peeling. Can be suppressed.

10 Journal bearing (slide bearing)
11, 11 ′, 11 ″, 12, 13, 14 Journal bearing member (bearing member)
11a, 11′a, 11 ″ a Lining layer (surface layer)
11b, 11′b, 11 ″ b Intermediate layer 11c Back metal layer (back layer)
11d Front edge portion 11e Rear edge portion 20 Thrust bearing (slide bearing)
21, 21 ′, 21 ″, 22, 23, 24 Thrust bearing member (bearing member)
21a, 21′a, 21 ″ a Lining layer (surface layer)
21b, 21′b, 21 ″ b Intermediate layer 21c Back metal layer (back layer)
21d Front edge portion 21e Rear edge portion 30 Rotor 30a Shaft portion (rotating portion)
30b Thrust collar (rotating part)
40 Support ring (fixing member)
50 Support member (fixing member)
A axis

Claims (8)

A rotor having a rotating part that rotates around an axis;
A sliding bearing comprising a bearing member supported by a fixed member and supporting a load applied to the rotor by forming a film of lubricating fluid between the rotating part and
The bearing member includes a surface layer formed of a resin material and a sliding surface in contact with the outer peripheral surface of the rotor, and a back layer formed of a metal material while supporting the surface layer.
The slide bearing according to claim 1, wherein a thickness of the surface layer at a rear edge portion of the bearing member is thinner than a thickness of the surface layer at a front edge portion of the bearing member. The bearing member includes an intermediate layer formed of a metal material between the surface layer and the back layer,
The plain bearing according to claim 1, wherein the hardness of the metal material forming the intermediate layer is lower than the hardness of the metal material forming the back layer.   The sliding bearing according to claim 1 or 2, wherein the thickness of the surface layer gradually decreases from the front edge portion toward the rear edge portion. A plurality of the bearing members are arranged at intervals around the axis along the outer peripheral surface of the rotor,
The sliding bearing according to any one of claims 1 to 3, wherein an outer peripheral surface of the rotor is supported by the plurality of bearing members.   The slide bearing according to claim 4, wherein a thickness of the surface layer at a central portion in the axial direction of the rear edge portion is thinner than a thickness of the surface layer at the front edge portion. The rotor includes a thrust collar for transmitting a load acting in the axial direction to the bearing member;
A plurality of the bearing members are arranged at intervals around the axis along the axial end surface of the thrust collar,
4. The plain bearing according to claim 1, wherein an end face of the thrust collar in the axial direction is supported by the plurality of bearing members. 5. The thickness of the surface layer on the inner peripheral side of the rear edge is thinner than the thickness of the surface layer on the inner peripheral side of the front edge,
The thickness of the surface layer on the outer peripheral side of the front edge portion and the thickness of the surface layer on the outer peripheral side of the rear edge portion are thinner than the thickness of the surface layer on the inner peripheral side of the front edge portion, respectively. A plain bearing according to claim 6.   A rotary machine provided with the sliding bearing of any one of Claims 1-7.

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